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US20060165522A1 - Centrifugal pump, in particular a spirally-housed centrifugal pump for a heat exchange medium - Google Patents

Centrifugal pump, in particular a spirally-housed centrifugal pump for a heat exchange medium Download PDF

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Publication number
US20060165522A1
US20060165522A1 US10/276,581 US27658105A US2006165522A1 US 20060165522 A1 US20060165522 A1 US 20060165522A1 US 27658105 A US27658105 A US 27658105A US 2006165522 A1 US2006165522 A1 US 2006165522A1
Authority
US
United States
Prior art keywords
centrifugal pump
shaft
pump
bearing
set forth
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/276,581
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English (en)
Inventor
Stefan Werner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Allweiler GmbH
Original Assignee
Allweiler AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Allweiler AG filed Critical Allweiler AG
Assigned to ALLWEILER AG reassignment ALLWEILER AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WERNER, STEFAN
Publication of US20060165522A1 publication Critical patent/US20060165522A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/0462—Bearing cartridges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5893—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps heat insulation or conduction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals

Definitions

  • the invention concerns a centrifugal pump—in particular a spiral-casing centrifugal pump—for a heat carrier medium, comprising a spiral casing having an impeller, a casing cover and an associated casing attachment portion for a pump shaft provided with a shaft bearing near the spiral casing and a shaft seal disposed at a spacing in relation to the shaft bearing in a sealing chamber.
  • a centrifugal pump in particular a spiral-casing centrifugal pump—for a heat carrier medium, comprising a spiral casing having an impeller, a casing cover and an associated casing attachment portion for a pump shaft provided with a shaft bearing near the spiral casing and a shaft seal disposed at a spacing in relation to the shaft bearing in a sealing chamber.
  • centrifugal pumps are described by way of example in a prospectus from the present applicants in relation to the range NHT for heat carrier purposes up to 350° C.
  • a spiral casing for an impeller is connected to a bearing casing by means of a throttle section having external ribs.
  • the impeller is fixed at one end of a pump shaft which extends in the throttle section.
  • a plain bearing of silicon carbide Arranged between the throttle section and the impeller is a plain bearing of silicon carbide and arranged downstream of the throttle section is a sliding ring seal which is followed by a rolling bearing.
  • This arrangement involves a horizontal spiral-casing centrifugal pump of a process type of structure which is single-stage in terms of intake flow.
  • the pump-side silicon carbide plain bearing is lubricated by the fluid being delivered, while used at the drive side is a grease-lubricated grooved-type ball bearing.
  • a bearing cup accommodating the shaft bearing, a tubular portion surrounding the pump shaft as a heat barrier and so-called support ribs or the like profile elements arranged at a spacing relative to each other in the peripheral direction are parts of the casing cover.
  • bearing cup is to be held at an axial spacing towards the impeller by the tubular portion which surrounds the pump shaft.
  • the sealing chamber for the shaft seal is advantageously delimited by the casing attachment portion which is preferably joined to the casing cover or an edge ring which is carried by the support ribs thereof and which surrounds the longitudinal axis of the pump; the edge ring is connected to and preferably integrally formed on the support ribs at their ends remote from the base region of the casing cover.
  • a latticework-like or trussing-like rib arrangement comprising those support ribs which are to be inclined towards the longitudinal axis from the spiral casing at a preferred angle of between 40° and 45° and—at a radial spacing relative to each other—surround the bearing cup and the heat barrier and form jointly therewith the casing cover.
  • the cross-sectional height of the support ribs which preferably extend in axial planes which pass radially through the longitudinal axis of the pump to be caused to increase towards the sliding ring seal in order to enhance the level of stability and minimise heat losses.
  • the sealing chamber is to adjoin the shaft bearing. Inter alia that ensures an adequate supply of lubricating medium to the bearing.
  • the bearing contributes to circulation of the medium in the sealing chamber for flushing and cooling the seal.
  • abutment step should preferably be a front ring which is formed on the casing cover.
  • An associated pump part can moreover be a spacer which extends around the bearing carrier casing and which abuts against the abutment step or steps or the front ring and to which a motor is attached.
  • the abutment step or the front ring prefferably be arranged to project from an annular flange which extends around the support ribs and which is mounted to the transition thereof to a base region of the casing cover.
  • the scope of the invention includes a centrifugal pump with a sealing ring of the shaft seal—in the form of a sliding ring seal—, the sealing ring extending therearound on a counterpart ring provided at the casing side; the counterpart ring is arranged for the sealing ring in a shaped stub portion of the casing attachment portion, the stub portion projecting axially into the sealing chamber.
  • a centrifugal pump with a sealing ring of the shaft seal—in the form of a sliding ring seal—, the sealing ring extending therearound on a counterpart ring provided at the casing side; the counterpart ring is arranged for the sealing ring in a shaped stub portion of the casing attachment portion, the stub portion projecting axially into the sealing chamber.
  • At last one opening or passage which is inclined with respect to the longitudinal axis of the pump and with a closure screw for closing it is to be associated with the stub portion—which is of an axial length approximately corresponding to half the axial length
  • the sliding ring seal is advanced within the sealing chamber in order to make available sufficient space for collecting air or outgassings of the delivery medium—in particular when the arrangement is positioned vertically.
  • the described arrangement of the passage with the closure screw easily permits complete venting of the sealing chamber both when the pump is positioned horizontally and also vertically.
  • the frictional heat of the sliding ring seal is desirably dissipated to the surroundings by virtue of a large surface area of the surrounding sealing chamber and a large volume of fluid in the sealing chamber.
  • the shaft bearing is in the form of a plain bearing with a ratio of the length of the bearing bush to the diameter of the pump shaft of between about 1.5 and 2.0, preferably about 1.8.
  • the bearing bush of the plain bearing should be designed to be dismantled.
  • the plain bearing as viewed from the impeller, is disposed behind the heat barrier, which contributes to simplicity of possible fixing and also contributes to the heat barrier being of a desirable design configuration.
  • the positioning of the impeller-side bearing behind the heat barrier means that the delivery medium which serves as a lubricating agent is at a lower temperature at that location than in the pump casing. As a result it is of higher viscosity, which is advantageous for the lubricating capability. In addition the vapor pressure of the medium at that location is markedly lower than in the pump casing, thereby minimising the risk of the bearing running dry.
  • the plain bearing or the bearing bush thereof for fixing purposes, to be surrounded approximately at the longitudinal center thereof on the outside by a clamping or tolerance ring which engages into the bearing cup.
  • the width of the clamping or tolerance ring should correspond to a fraction of the length of the bearing bush, for example between a fifth and a sixth of the length of the bearing bush. That provides for easy (dis-)mantling as well as compensation for alignment errors by virtue of tilting mobility.
  • the plain bearing includes an inner bearing sleeve which is surrounded by a bearing bush at the bearing cup side.
  • the pump shaft is surrounded within the plain bearing by at least one tolerance ring which engages into the pump shaft.
  • an inward tolerance ring should be provided on each of the two sides of the outer tolerance ring which engages into the bearing cup—as viewed in longitudinal section of the centrifugal pump—, the inward tolerance ring engaging into the pump shaft.
  • the bearing sleeve and the bearing bush are preferably made from silicon carbide.
  • Another design configuration in accordance with the invention involves a plain bearing with a bearing bush at the bearing cup side, the bearing bush including a slidable internal peripheral surface portion which extends around the pump shaft.
  • the dismantleable plain bearing bush is preferably provided with an inner carbon coating.
  • the bush runs on a hardened shaft or a hardened shaft portion. Fixing is effected by a centrally disposed outer tolerance ring, as already mentioned.
  • the sliding ring seal extends around a shaft sleeve at the shaft side, wherein at least one O-ring is provided between the shaft sleeve and the pump shaft. That arrangement, in a construction which is relieved of load, permits assembly of the sliding ring seal from the impeller side, which is desirable in particular when the shaft is in the form of a plug-in shaft.
  • a rearward shaft bearing for the pump shaft arranged in the casing attachment portion at an axial spacing relative to the sliding ring seal outside the sealing chamber is a rearward shaft bearing for the pump shaft; at least one hollow space can also be provided in the casing attachment portion between the sealing chamber and the shaft bearing.
  • the pump shaft is in the form of a plug-in shaft with clamping ring.
  • FIGS. 1 and 8 each show a perspective view of different embodiments of a centrifugal pump according to the invention for heat carrier media
  • FIG. 2 shows an end view of the FIG. 1 structure
  • FIG. 3 shows a partial longitudinal section through FIG. 2 along line III-III therein
  • FIG. 4 shows a view in longitudinal section on an enlarged scale through the pump in FIG. 2 taken along line IV-IV therein,
  • FIG. 5 shows a view on an enlarged scale of a part of the FIG. 4 structure
  • FIG. 6 shows a longitudinal section corresponding to FIG. 4 through another embodiment of the pump shown in FIG. 1 ,
  • FIG. 7 shows a view on an enlarged scale of a portion of the FIG. 6 structure
  • FIG. 9 shows an end view of the FIG. 8 structure
  • FIG. 10 shows a perspective view of a casing cover of the pump
  • FIG. 11 shows a view on an enlarged scale through the pump of FIGS. 8 and 9 taken along line XI-XI in FIG. 9 ,
  • FIG. 12 shows a partial longitudinal section on an enlarged scale in relation to FIG. 11 taken along line XII-XII in FIG. 9 ,
  • FIGS. 13 and 14 show different perspective views of a part of a further embodiment of a centrifugal pump according to the invention
  • FIG. 15 shows an end view of the structure shown in FIGS. 13 and 14 .
  • FIG. 16 shows a partial longitudinal section through the pump of FIGS. 13 through 15 taken along line XVI-XVI in FIG. 15 , and
  • FIG. 17 shows a partial section on an enlarged scale in relation to FIG. 16 through that pump taken along line XVII-XVII in FIG. 15 .
  • a spiral-casing centrifugal pump 10 on a volute or spiral casing 14 provided with connecting flanges 12 , 12 a ,—with the interposition of seals (not shown)—has a bearing carrier casing 16 which includes a casing cover 18 with a casing attachment portion 34 fitted thereto.
  • the casing cover 18 is provided with an annular flange 21 which projects from a dish-like base region 20 and through which pass connecting screws 24 , on a front ring 22 which is formed on the annular flange 21 and which forms an abutment step; the connecting screws 24 are fitted into sleeve ribs 15 which are formed in axis-parallel relationship externally on a peripheral wall 13 of the spiral casing 14 , the peripheral wall engaging over the dish wall 19 , and the screws 24 centeringly connect the casing cover 18 to the spiral casing 14 .
  • support ribs 26 Formed on the casing cover 18 or the base region 20 thereof respectively are support ribs 26 of substantially constant thickness b, which are determined by axial planes E—passing radially through the longitudinal axis A of the pump—and which are inclined at an angle w of about 40° towards the longitudinal axis A of the pump.
  • the cross-sectional height h of the support ribs 26 steadily increases in the longitudinal extent or in the axial direction away from the casing cover 18 .
  • the support ribs 26 are cast at the other end to a bearing cup 28 axially associated with the longitudinal axis A of the pump and an edge ring 30 which surrounds the bearing cup.
  • An axial tubular portion 32 which is integral with the casing cover 18 connects the bearing cup 28 thereto, in centered relationship.
  • the bearing cup 28 , with its edge ring 30 , and the support rings 26 are also part of the casing cover 18 whose length a, approximately corresponds to a third of the pump length a.
  • a pump shaft 36 of a diameter d Passing through the casing cover 18 and the rearward casing attachment portion 34 —that is to say the bearing carrier casing 16 —is a pump shaft 36 of a diameter d, while an impeller 40 is held on the front stepped end 37 thereof by a nut 38 .
  • the impeller 40 rotates in the spiral casing 14 which includes an intake or suction chamber 42 , whose inlet in the region of the axial connecting flange 12 is identified by reference 43 and whose radial outlet in the connecting flange 12 a is identified by reference 44 .
  • a stuffing-box packing 46 Disposed near the impeller 40 in the casing cover 18 is a stuffing-box packing 46 at the periphery of the cylindrical tubular portion 32 .
  • the internal space 29 of the bearing cup 28 is connected to the cylindrical tubular portion 32 which extends around the pump shaft 36 to form a heat barrier. If for example a flow agent of low viscosity at about 350° C. passes through the inlet 43 , flow agent of higher viscosity at 130° C. is disposed in the internal space of the bearing cup.
  • the internal space 29 of the bearing cup 28 which adjoins the cylindrical tube portion 32 , communicates with a sealing chamber 48 which is arranged in the bearing carrier casing 16 or in the casing attachment portion 34 and which is surrounded by an annular wall 50 and which is provided with at least one closure screw 52 together with a screwthreaded opening or passage 53 which accommodates the screw and which is inclined at an angle z of 45° relative to the longitudinal axis A of the pump, and with blade-like surface elements 55 which are inclined relative to each other and which each have a respective edge 54 parallel to the axis, the axial length e 1 thereof approximately corresponding to half the length e of the casing attachment portion 34 .
  • FIG. 2 shows a lateral closure screw 52 a which is required for venting when the pump 10 is used in a vertical position.
  • a rear axial sliding ring seal 56 which is not relieved of load—can be seen in the sealing chamber 48 .
  • annular wall 50 Projecting from the annular wall 50 are four radial lugs 51 which are connected to corresponding counterpart lugs 51 a of the edge ring 30 by screws 24 a .
  • annular flange can also be provided, instead of the above-mentioned radial lugs 51 .
  • axially extending surface portions can be arranged on the outside of the annular wall.
  • the sliding ring seal 56 includes a coil spring 58 —which is supported against a ring step or a ring 38 which is pushed on to the pump shaft 36 —and which loads a rotating sliding ring 59 which with a stationary counterpart ring 60 forms a sealing gap.
  • the counterpart ring 60 is disposed in the tubular space 62 of an axial shaped stub portion 64 of an axial length f which here corresponds approximately to half the sealing chamber length e 1 .
  • a dish-like hollow space 66 Arranged subsequently to the annular end part 65 of the stub portion 64 in the casing attachment portion 34 is a dish-like hollow space 66 .
  • the pump shaft 36 is surrounded by a grooved-type ball bearing 68 with spacer disks 69 and a securing ring 70 ; that unit is covered by a bearing cover 72 of the casing attachment portion 34 .
  • a plate-like support leg 74 Projecting radially beneath the latter is a plate-like support leg 74 which is fixed by screws 24 b , comprising an angle plate member, in opposite relationship to which, in the region of the spiral casing 14 , are two supports 74 a which project in parallel in eccentric relationship.
  • the supports 74 a and the support leg 74 are connected at the other end to a base plate (not shown).
  • a front hydrodynamic plain bearing 76 comprising a bearing bush 77 of a length g with an internal peripheral surface portion 78 of carbon material; the plain bearing 78 , at its longitudinal center, is surrounded by a clamping or tolerance ring 80 of a width n, the ring 80 being provided in the bearing cup 28 —that is to say at the housing side—; the ring 80 is of an elastic nature and force-lockingly connects the plain bearing 76 to the bearing cup.
  • the plain bearing 76 a of the pump 10 a as shown in FIGS. 6 and 7 has within the bearing bush 77 a coaxial bearing sleeve 82 and—besides the above-described outer tolerance ring 80 at the longitudinal center—two inner tolerance rings 80 i of a width i which are disposed at the shaft side and which—viewed in longitudinal section—flank the outer tolerance ring 80 at the pump shaft 36 at a radial spacing on both sides.
  • the width n of the outer tolerance ring 80 and the width i of the inner tolerance rings 80 i are relatively short in relation to the length g of the bearing bush, for example the latter corresponds approximately to between five and six times the width i and n respectively.
  • Reference 84 in FIGS. 6 and 7 shows a nut which is disposed between the front plain bearing 76 a and the rear sliding ring seal 56 —which is here relieved of load—for the purposes of fixing the bearing sleeve 82 .
  • the sliding ring components for carrying the radial forces which occur preferably comprise silicon carbide in the illustrated embodiment.
  • the two above-discussed bearing types 76 , 76 a can also be used in the centrifugal pump 11 shown in FIGS. 8 through 12 in which the pump shaft 35 is in the form of a plug-in or stub shaft and is provided with an O-ring 88 within a shaft sleeve 86 of the sliding ring seal 56 a , the shaft sleeve 86 surrounding the pump shaft.
  • the O-ring 88 is disposed between the pump shaft 35 and a shaft sleeve 89 embracing it.
  • the pump shaft 35 includes a clamping ring 92 which carries a fan wheel 90 and which is surrounded towards the front by a protective grid 93 as protection to prevent articles from being poked in.
  • the impeller 90 is surrounded by a wall ring 94 —with apertured plate members 95 —of a spacer 96 with endward flange rings 97 , 97 a ; they are connected by longitudinal ribs 98 which are parallel to the axis.
  • the flange ring 97 which is at the right in the drawing is screwed to a parallel flange ring 99 of a motor 100 , the flange ring 99 bearing against the spiral casing 14 ; the motor 100 is fixed by means of the spacer 96 to the pump 11 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US10/276,581 2001-04-26 2002-04-26 Centrifugal pump, in particular a spirally-housed centrifugal pump for a heat exchange medium Abandoned US20060165522A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10120543.0 2001-04-26
PCT/EP2002/004667 WO2003091572A1 (de) 2002-04-26 2002-04-26 Kreiselpumpe, insbesondere spiralgehäuse-kreilselpumpe für ein wärmeträgermedium

Publications (1)

Publication Number Publication Date
US20060165522A1 true US20060165522A1 (en) 2006-07-27

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Application Number Title Priority Date Filing Date
US10/276,581 Abandoned US20060165522A1 (en) 2001-04-26 2002-04-26 Centrifugal pump, in particular a spirally-housed centrifugal pump for a heat exchange medium

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US (1) US20060165522A1 (de)
AU (1) AU2002302582A1 (de)
WO (1) WO2003091572A1 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010111357A3 (en) * 2009-03-24 2011-01-13 Concepts Eti, Inc. High-flow-capacity centrifugal hydrogen gas compression systems, methods and components therefor
US20120001444A1 (en) * 2008-06-13 2012-01-05 Micheal Christopher Foreman Improvements relating to pump seal assemblies
CN107218253A (zh) * 2017-07-11 2017-09-29 武安市永盛机械泵业有限公司 一种含有降温轴承体装置的热媒泵
CN110709609A (zh) * 2017-06-09 2020-01-17 Ksb股份有限公司 用于输送热介质的离心泵
CN117345655A (zh) * 2023-12-05 2024-01-05 四川川工泵业有限公司 一种泵撬
US12360643B2 (en) * 2021-02-22 2025-07-15 KSB SE & Co. KGaA Pump having a control panel

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104500437A (zh) * 2014-12-01 2015-04-08 安徽凯特泵业有限公司 一种高温酸泵的叶轮安装结构
CN106640727A (zh) * 2016-11-30 2017-05-10 江苏振华泵业股份有限公司 船用卧式离心泵内置降温式轴承座

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6402462B1 (en) * 1997-11-17 2002-06-11 Allweiler Ag Centrifugal pump with a floating ring seal

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CH393928A (de) * 1961-08-02 1965-06-15 Klein Schanzlin & Becker Ag Kreiselpumpe, insbesondere zur Förderung heisser Flüssigkeiten
US3554661A (en) * 1968-12-20 1971-01-12 Decatur Pump Co High temperature pump
DE2113747A1 (de) * 1971-03-22 1972-09-28 Allweiler Ag Kreiselpumpe
DE2140959A1 (de) * 1971-08-16 1973-03-01 Allweiler Ag Einrichtung zum spuelen der wellenabdichtung an einer kreiselpumpe
GB8909504D0 (en) * 1989-04-26 1989-06-14 Weir Pumps Ltd Pump with seal cooling means
JPH0664183B2 (ja) * 1990-10-26 1994-08-22 株式会社荏原製作所 高温ポンプの熱疲労防止装置
FR2756328B1 (fr) * 1996-11-22 1998-12-31 Jeumont Ind Barriere thermique de pompe primaire
DE10057183A1 (de) * 2000-11-17 2002-05-23 Ksb Ag Magnetkupplungspumpe für heiße Fördermedien

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Publication number Priority date Publication date Assignee Title
US6402462B1 (en) * 1997-11-17 2002-06-11 Allweiler Ag Centrifugal pump with a floating ring seal

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120001444A1 (en) * 2008-06-13 2012-01-05 Micheal Christopher Foreman Improvements relating to pump seal assemblies
US8662551B2 (en) * 2008-06-13 2014-03-04 Weir Minerals Australia Ltd. Improvements relating to pump seal assemblies
WO2010111357A3 (en) * 2009-03-24 2011-01-13 Concepts Eti, Inc. High-flow-capacity centrifugal hydrogen gas compression systems, methods and components therefor
US20120011857A1 (en) * 2009-03-24 2012-01-19 Concepts Eti, Inc. High-Flow-Capacity Centrifugal Hydrogen Gas Compression Systems, Methods and Components Therefor
US9316228B2 (en) * 2009-03-24 2016-04-19 Concepts Nrec, Llc High-flow-capacity centrifugal hydrogen gas compression systems, methods and components therefor
US10526964B2 (en) 2009-03-24 2020-01-07 Concepts Nrec, Llc High-flow-capacity centrifugal hydrogen gas compression systems, methods and components therefor
CN110709609A (zh) * 2017-06-09 2020-01-17 Ksb股份有限公司 用于输送热介质的离心泵
CN107218253A (zh) * 2017-07-11 2017-09-29 武安市永盛机械泵业有限公司 一种含有降温轴承体装置的热媒泵
US12360643B2 (en) * 2021-02-22 2025-07-15 KSB SE & Co. KGaA Pump having a control panel
CN117345655A (zh) * 2023-12-05 2024-01-05 四川川工泵业有限公司 一种泵撬

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Publication number Publication date
AU2002302582A1 (en) 2003-11-10
WO2003091572A1 (de) 2003-11-06

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Legal Events

Date Code Title Description
AS Assignment

Owner name: ALLWEILER AG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WERNER, STEFAN;REEL/FRAME:014279/0945

Effective date: 20021112

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION